Apparatus for grooving and/or longitudinally cutting a continuous web

ABSTRACT

An apparatus for longitudinally deforming webs of paper, cardboard and the like and especially of corrugated board. The main object of the invention is to adjust the positioning of the tools and thereby to form the basis for automatically preselecting and adjusting the tools of such machines. These tools for longitudinally deforming said web may be either grooving, cutting or slitting tools. For solving this problem, the tools and the tool shafts are screw threaded, and means are provided for clamping said tools on said tool shafts for achieving the working condition. Servo motors including coupling and braking means are provided for actuating the adjustment of said tools. Substantially mechanical means including compressed air operated nozzles form the basis for a highly efficient, reliable and likewise simple device to preselect the different positions of the tools.

Umted States Patent 1 91 1 3,760,697 Besemann 1 Sept. 25, 1973 [54] APPARATUS FOR GROOVING AND/0R 3,332,326 7/1967 Haas 93/582 R LONGITUDINALLY CUTTING A gig gig m CONTINUOUS WEB 3:587:374 6/1971 Stewart 83/499 x [75] Inventor: Alfred Besemann, Hamburg,

Germany Primary ExaminerFrank T. Yost [73] Assignee: Werner H. K. Peters Anomey Beaman & Beaman Maschinenfabrik G'.m.b.H., Hamburg, Germany [57] A T An apparatus for longltudmally deformmg webs of pa- [22] Flled: 1971 per, cardboard and the like and especially of corru- 2 APPL 1 57 gated board. The main object of the invention is to adjust the positioning of the tools and thereby to form the basis for automatically preselecting and adjusting the [30] Foreign Application Prlorlty Data tools of such machines Sept. 26, 1970 Germany P 20 47 503.0 These tools for longitudinally deforming said web y U S Cl 93/58 2 R 83/425 4 be either grooving, cutting or slitting tools.

f 83/4228 For solving this problem, the tools and the tool shafts s 1 Int. Cl. B26d 1/24 B2 6d 5/02 are Screw threaded, and means Pmvided 581' Field of Search 93/582 R 58.1- clampingsaid tlshafts achieving the 83/428 499 498 working condition. Servo motors including coupling and braking means are provided for actuating the [56] References Cited adjustment of said tools. Substantially mechanical means including compressed air operated nozzles form UNITED STATES PATENTS the basis for a highly efficient, reliable and likewise gndgmanmsimple device to preselect the different positions of the I uncan I 2,969,930 1/1961 Zernov.... 83/428 x 3,147,676 9/ 1964 12 Claims,'l0 Drawing Figures Sheeran 83/499 X PATENTEU'SEPZ 5 i973 saw u or s fig-i PATENTEDSEPZSIQH 3.760697 sum 5 or e PAFENTED SEPZ 5 I973 SHEET S [If 6 APPARATUS FOR GROOVING AND/OR LONGITUDINALLY CUTTING A CONTINUOUS WEB The invention relates to an apparatus for grooving and/or longitudinally cutting a continuous web of cardboard, paper or the like, comprising at least one tool shaft extending transversely of the path of movement of the web and rotatably supported at the machine stand, grooving and/or cutting tools displaceably supported on the tool shaft, adjusting means for moving the tools, and control devices to control the adjusting means.

In the packaging industry, for example, continuous webs must be cut longitudinally into strips for the different blanks. In order to facilitate the folding of the blank, these strips are mostly provided additionally with longitudinally extending grooved lines. At known devices the cutting and grooving tools are fastened on continuous, essentially round, smooth shafts. To change the width of the strips or the position of the grooved lines, respectively, on the web, the tools are manually brought into a different position. Mostly there are a plurality of tools for grooving or cutting on one shaft. Smooth rolls which may also be provided with an elastic coating, or profilated counter rolls or counter cutters serve as counter tools. Especially, with sensitive webs, for instance corrugated board, the use of profilated grooving and counter-grooving tools has largely proved to be of good advantage. The adjustment of the large number of cutting or grooving tools is connected with a substantial loss of time when dimensions are to be changed. If the device is built-in in a production line, production flow will be decisively obstructed when the tools are to be adjusted. For this reason machine constructions have become known which work with several cutting and grooving units.

Mostly, two to three grooving and cutting units are rotatably arranged like a revolver about a center in the shape of a star. While one unit is in engagement with the continuously moving web, the other units may be pre-adjusted for the following orders.

If a change in dimension becomes necessary, then the moving web will be cut up. Thereupon the entire production speed is reduced almost to a standstill. The rearward portion of the web is accelerated to a somewhat higher speed. The revolver with the pre-adjusted tools moves in a swinging movement into the thus formed gap of the continuously moving web. After the forward end of the web has been introduced into the new tools the plant is again accelerated to production speed.

Apart from the positively occurring reduction in the production output, disadvantages occur especially in case of such production methods in which the continuously moving web is subjected to influences of heat and moisture. As the heating elements mostly have a great heat inertia, the imperatively necessary change in the production speed is at the same time effective to bring about an undesired change in the heat and moisture treatment, respectively, of the continuously moving web. This leads to waste being produced or a reduction in the quality of the blanks produced, and to difficulties in the further processing thereof in printing machines,

for example, especially when the blanks get curved by the change in temperature.

In addition to being displaced manually, the tools may be displaced on the round, smooth shafts by adjusting devices, said adjusting devices being movable back and forth on special adjusting spindles. Each tool has associated thereto a special spindle which are individually rotated by a coupling controlled by a control device, so that the tool carrier member reaches its desired position.

Owing to theplurality of transport spindles, couplings and the pertaining switching elements, these devices are very costly and in addition susceptible to trouble. Besides, safety in operation is very difficult to maintain because of the wear to which the many parts are subjected.

The invention is aimed at the provision of a device of the type mentioned which may be produced with little expense and which guarantees a high degree of safety in operation, and in which the tools may be positioned on the tool shaft with a sufficient degree of accuracy.

In accordance with the invention provision is made for the tool shaft to be designed as a spindle with a transport thread, while the carrier of the tool is a -nut which is selectively locatable on the spindle or may be retained thereon non-rotatably but capable of axial displacement.

With this arrangement, the many transport spindles which are arranged in parallel with the tool shaft are eliminated and there is only one spindle provided which simultaneously serves as the tool shaft. If now the tool shaft is rotated, all the tool members which are not located on the shaft and which are non-rotatably retained thereon, will move simultaneously in one and the same direction on the guide shaft. The individual members cannot run onto each other", because they are all of them subjected to the same feed. Those members which would remain in their positions or would be set prematurely, might be in danger of collision. At

first, the holding means of the tool carrier with the shorter transportpath are released through the control devices and thereafter the tool carrier is located on the spindle. The tool carrier and with it the tool remain in the thus selected position on the spindle. All the tool carriers are positioned in this manner one after the other by loosening the retaining means and locating the nut.

Preferably, the nut consists of two partial nuts one of which carries the tool, i.e. the cutting tool or the grooving form, said partial nuts being kept frictionally engaged with the flanks of the thread of the spindle by suitable means. The frictional forces occurring at the flanks are completely sufficient to keep the nut in its selected position on the tool shaft also during the process of production. The clamping means may be springs, in particular, which urge the two partial nuts as under and onto the flanks of the spindle shaft.

in order to abolish the frictional engagement between the partial nuts and the tool shaft, when the nut is to be displaced on the shaft, it is recommendable to support guide arms for displacement in the machine stand, said guide arms carrying guides which are adapted to be biased in a direction towards the partial nuts in response to a control signal in order to abolish the frictional engagement. Both, the frictional engagement of the partial nuts and a non-rotatable retention yet one permitting of axial displacement of the nuts, are achieved by these retaining elements.

As with the positioning of the too] carriers on the tool shaft absolute accuracy is not so much a point as that the tool carriers must be retained in the once selected position, it suffices when provision is made in accordance with the invention for the nut to be dislaceable by the adjustment means only by whole number multiples of a unit length in an axial direction of the tool shaft and in the sense of rotation of the tool shaft.

For positioning the tools, the tool carrier is provided with peripheral slots, especially the nuts are connected with separate slotted discs and the guide arms carry interlocking members, which are adapted to be introduced into the slots in response to a control signal.

Prior to the respective tool carrier obtaining its end position, the rotary feed of the transport shaft is switched to creeping speed. Subsequently, all the other tool carriers which are to be transported in the opposite direction are simultaneously brought into the new position through a movement of the tool shaft in the opposite direction of rotation and are gradually set in that position. Owing to the engagement of the interlocking pieces it is obtained that the tool carriers are displaced during the positioning step always only by whole number multiples of a unit length determined by the toothing of the slotted discs and the scew pitch of the transport thread. In addition, co-rotation during the positioning step is additionally prevented thereby.

In a suitable embodiment, the guide arms are pivotally interconnected at one end and carry the interlocking members adjacent the other end, with a device provided for moving the arms towards each other and away from each other. This device may again be constituted by a piston and cylinder motor.

The control device is responsible for actuation of the piston-and-cylinder drives to bias the guides to overcome the tensional forces and for bringing the interlooking members in engagement with the slots on the I cision on the sense of rotation of the adjusting motor,

a downshift being effected in a transmission or coupling system with a standstill subsequently taking place when an actual value approaches the rated value.

In a preferred embodiment of the invention an actual value slide displaceable by means of a control transport spindle is provided for each tool, in which the transport spindle is non-rotatably connected with the tool shaft; the actual value slide being provided with a control nozzle system andone rated value slide per tool being provided with covers which cover the control nozzles when the two slides approach each other. The control nozzle system in connection with the sheets for covering the air nozzles serves as a link between the signal member and the first control member.

As the controltransport spindle is to be accommodated in a preselection desk, it is desirable for said spindle not to have the same length as the tool shaft. Therefore, provision has been made for the transport control ated and is easy to overlook. If the actual value slides,

are arranged in such a manner that they are likewise visible on the surface of the control desk, one may overlook all the newly selected positions and the respectively available actual values.

The number of control nozzles is selected to be such that a decision is taken on the sense of rotation of the motor in the preselection system, and when the two slides approach each other the speed is first slowed down and then rotation at creeping speed takes place. The motor is then stopped through a brake at the control transport spindle and the stopping point is fixed by means of an arresting disc. The control nozzle system -in this arrangement has series-connected thereto an electric or pneumonic logic which processes the signals resulting from the cooperation of the control nozzles and the covering means.

It is possible with the aid of the nozzle system to produce an element of automation extremely safe in operation with relatively simple technical means. As already explained, the rated value slides may be moved into the desired positions via known electronic devices, the punch cards, punched tapes etc. being employed as data carriers. So that the feed of the tool shaft may be regulated in such a manner that the rotary transmission may stop the feed only in rhythm with the respective stitches, a toothed control disc is fastened on the tool shaft which is provided with the same number of slots as the slotted disc and a light source photoelement arrangement is provided which issues a signal in response to the angle of rotation of the control disc with the aid of which the control device controls the rotation of the adjusting motor in such a manner that the latter displaces the tools only in rhythm with the slots.

In order to obtain at the beginning of the positioning step a defined starting position of the tool shaft, there is an adjusting slot disc fastened on the tool shaft, into the slots of which a bar may be introduced, in order to bring the shaft and with it the slotted disc into a position which corresponds to the whole number pitch.

In one embodiment of the invention the tools are working against smooth shafts or counter members. However, embodiments may also be imagined having two tool shafts, with one shaft having the tools arranged thereon and the other one the counter tools in a manner known per se which are cooperating as pairs.

With this device it is recommendable to adjust the tools and counter tools simultaneously on their shafts. For this purpose, the arrangements and devices which have been mentioned so far will have to be transferred to the counter tool shaft. The piston-and-cylinder drives, which are associated with the counter tool carrier, are controlled simultaneously with the piston-andcylinder drives which are associated with the tool carriers. Owing to this arrangement absolutely equal paths of adjustment are obtained with a few parts and little technical means.

As a plurality of fluid carrying hose lines must be guided to each pair of guide arms, and as these guide arms change their spaces from the machine stands when the positioning steps are carried out, a possibly simple but movable line system should be made use of.

Therefore, the device in accordance with the invention is characterized by at least one disc rotatably supportedon a shaft in the machine stand to accommodate a flexible fluid line to the periphery of the disc connected at one end thereof with a fluid source and at the other end to a piston-and-cylinder arrangement cooperating with the guide arms, with the disc while being loosely frictionally engaged biased in the sense of rotation tightening the end of the hose line leading to the piston-and-cylinder drive, and with the line tightly clamped at the disc without separation.

Such a manner of supplying the guide arms with fluid pressure can do without any sliding sealing. Owing to this device, it is achieved in an economical manner and with a high degree of safety, that the hose is constantly tightened but does not have to be interrupted in any place, so that a simple connection is possible between the pressure source and the piston-and-cylinder drive to be operated.

Preferably, there is a control valve formed between the clamping place and the pressure source with the line between the clamping point and the control valve extending in a very loose loop.

In a suitable embodiment of the invention there are several discs for fluid lines combined on a shaft to form a transport barrel. With this it is possible for the discs to be individually subjected to the loose frictional engagement independently of each other, or for several discs to be connected with each other.

In order to align the lines in a direction towards the guide arms it is recommendable to guide the hose line between disc and guide arms over at least one deviation roller.

As the device is to be especially simple in construction and production is to furthermore in an economical way, the cutter tools in accordance with the invention consist of thin elastic annular discs which are fastened on the tool carrier. Preferably, the device is designed in such a manner that when working with tool and counter tool, the annular discs resiliently contact each other in their working position.

As with the devices of the type mentioned one transport shaft is adapted to be moved towards the other, the annular cutters may be positioned to move past each other with a certain space of safety between them when they are moved towards each other. If now the one shaft is supported for axial displacement in accordance with the invention, it is possible for the one shaft to be moved axially by a slight degree in the direction of the other cutter at the very moment when overlapping is obtained. Owing to the resilient bias which may be built up by the two cutters contacting each other, the residual tolerances may be bridged over.

In order to avoid with cutters cooperating in such a manner a tearing-up or vaulting of the web to be cut in the cutting region, provision has been made in accordance with the invention to support the web to be cut by a portion of the cylindrical tool carrier.

The device in accordance with the invention will now be described in detail by way of some Figures in such a manner that the inventive features and further advantages of the invention will become clearly visible. In the Figures,

FIG. 1 is a partly sectional diagrammatic side view of the one end of a device according to the invention with an upper and a lower tool shaft;

FIG. la a detail, sectional view of the device in accordance with the invention in which the cutters and counter cutters contact each other;

FIG. lb a detail, sectional view of the device in accordance with the invention on an enlarged scale, in which the cutters and counter cutters contact each other but with a part of the bipartite nut deviating in shape,

FIG. 2 a detail sectional view of the thread of the upper and lower tool shafts on an enlarged scale;

FIG. 3 an elevational sectional representation of the retaining and positioning means with the retaining means open;

FIG. 3a an elevational sectional view of the retaining and positioning means with the retaining means closed;

FIG. 4 a diagrammatical and partly sectional view of the other end of an upper and lower shaft, with the grooving tools fitted on the shafts and the different parts of the control device shown,

FIG. 5 a cross-sectional view of a device similar to the sectional view taken along line 55 in FIG. 6;

FIG. 6 a plan view of an embodiment of the device in accordance with the invention looking in the direction of the transport of the web to be processed, and

FIG. 7 a partly cross sectional view along line 7-7 in FIG. 6.

In FIGS. 1 and 4, which are at first dealt with for describing the support of the tool shafts, the drive and the control, the upper transport and tool shaft 1 is respectively supported right and left in the lateral stands 2 and 3. The lower transport and tool shaft 4 is movably supported in slots in the lateral stands 2 and 3 so that it is possible for the tools arranged on the shafts 1 and 4 to be moved towards each other and away from each other. FIG. 1 shows the cutter tool and counter cutter tool, respectively carrying a cutter 5a and a counter cutter 5b.

FIG. 4 shows the grooving tool and the counter grooving tool carrying a grooving form 6a or a counter grooving form 6b. So that the shaft 4 may be moved towards the shaft 1 and separated therefrom, the shaft drive is connected with the drive shaft 7a via a movable coupling 7. The shaft 7a is connected with the main drive 10 via a transmission 9 with the aid of a coupling switch 8.

In the embodiments shown in the Figures, the upper shaft 1 and the lower shaft 4 are provided with a transport thread 11. On the transport thread 11 there are situated the nuts consisting of partial nuts 12 and 13 of which the one carries the tool 5a or 512, and 6a or 6b, respectively. The nut 13 may, for instance, consist of the nut member 13a proper and a ring 13b which are screwed with each other by bolts l3cand clamp between them the annular cutters 5a and 5b. In the case of grooving tools, the grooving forms are likewise screwed to one of the partial nuts 12 or 13.

As will be described in more detail hereinafter guide arms are supported in the machine stand loosely following the tool movement (please see FIGS. 3 and 3a), namely the arms 15a and 15b. Such arms are provided for all the tool carriers. The parts 15a and 15b are connected in apivot point and may pivot open and are urged away from each other in accordance with FIG. 30 by means of a spring 51a. Clamping plates 18 are fastened at the end of the guide arms 15a, 15b which grips over a slotted disc 34 connected with the nut 12, 13. With the shear-like opening, interlocking members 35 connected with the guide arms 15a and 15b may be disengaged from their engagement in the slotted discs, as is shown in FIG. 3a. At the two open ends of the guide arms 15a, 15b, there is respectively disposed a clamping plate 18a or 18b. The clamping plate and the guide arm are urged away from each other by springs 14 and 16, so that they have no contact with the partial nuts 12 and 13.

If the clamping plates and guide arms are pressed together by forces effective from outside, which are indicated in FIG. 3 in the form of four cylinder drives 17 and a cylinder drive 51, then the partial nuts 12 and 13 are pressed together via the clamping plates 18a and 18b connected with the guide arm members 15a and 15b contrary to the force of the spring 14 so much that the frictional engagement of the partial nuts with the thread 11 is abolished.

If now the adjustment of the now frictionally engaged tool carriers is to take place, the coupling 8 will be disengaged prior to engagement of the guide arms, so that there is not longer any connection with the main drive 10. A transmission 20a, 20b and 200 is connected with the adjusting motor 21 through the coupling 19a, 19b and 190. Ones of the wheels of the transmission 20a, b, c are seated on a shaft 22a, which is non-rotatably connected with the upper tool shaft 1. After tightening the coupling 190, the control motor may rotate the upper transport shaft and simultaneously the lower transport shaft 4, because there is a gear 22 arranged on the shaft 22a and a gear 23 on the shaft 7a, said gears being in mesh with each other.

The shafts 1 and 4 and thus the tool carriers are moved in an overdrive speed via the coupling stage 19c and the transmission 200. As the tool carriers get near the desired position the coupling 19c is opened and the coupling 19b closed. The tool carrier is then moved at a slow driving speed. Immediately before it reaches the desired position the coupling 19b disengages and the coupling 19a engages. The tool carriers are now moving at a creeping speed via the transmission 20a.

When the tool carriers have reached the desired position, the coupling 19a opens and closes the brake 50, one part of which is connected with the shaft 220. Subsequently the piston-and-cylinder drives 17 and 51 are actuated in such a manner that the guides 15a, 15b and the clamping plates 18a and 18b leave their engagement with the two partial nuts so that the springs may press the split nut again into the leads of the thread and fixedly position it therein.

FIG. 1a shows the'working position of the tool carriers and the cutters, respectively. After the connections with the control motor have been loosened by the couplings 19a, b, c, the coupling 8 is closed, so that the connection with the main drive motor is again established.

such a distance that the tools and 6, respectively, engage with the web of material passing through. The parted guide arms have no fixed contact with the parted nuts during production.

So that the guide arms a and 15b when getting arrested again with respect to the slotted discs 34 which are likewise arranged on the shafts 1 and 4, respectively each beside one of the partial nuts and connected therewith, remain in a favourable arresting postion for the interlocking members 35 provided on the arm members 15a and 15b, the guide arms are tightly clamped by means of wedges 29 and adjusted on the carriers 27 and 28 which extend between the machine frames 2 and 3. While the interlocking members 35 are being arrested, these wedges 29 are loosened. After completion of the positioning step the guide arms which are pivotally connected with each other at one end are urged away from each other by the spring 51a at the piston and cylinder drive 51 in the direction of the arrow 54 until the interlocking pieces 35 release the slots of the slotted disc 34. The end position of the guide arms 15 is determined by the stops 52 and 53, respectively, which are provided on the longitudinal beams 27, 28.

FIG. 4 shows the control device. A slotted disc 30 is rigidly connected with the upper tool shaft 1. An indicator system 31 of which the light source and a photoelement are arranged on different sides of the slotted disc 30 controls the couplings 19a, b, c and the brake 50' in such a manner that the shafts 1 and 4 are stopped only with a full slot pitch. Before the positioning step is initiated by moving the parts 15a, 15b and 28a, 18b of the parted guide arms 15 towards each other, bars 32 become arrested in slotted discs rigidly connected with the transport shafts 1 and 4. So that the bar 32 for the shaft 4 always hits in the same position, there is provided a fixed lower stop 62 for the lower shaft 4. An upper stop 63 is adjustable for the different thicknesses of cardboard. Because of this it is guaranteed that the slotted discs 34 (please see FIG. 3) which are provided with the same number of slots as the slotted disc 33, are always in a position corresponding to a whole number pitch of the slotted discs. An embodiment may also be imagined in which the bar is a double bar 32 which also engages in a second slotted disc 33 provided on the lower transport shaft. The positioning of the tool carrier in a whole number pitch is secured by the interlocking members 35 provided at the parted guide arms 15 snapping into the slots of the slotted disc 34. The pitch of the slotted discs 34 in connection with the lead of the transport shafts l and 4 is selected to be such that one slot pitch corresponds to a fixed measurement,

for instance, 1 mm. Because of this it is obtained with I favourable technical means that positioning of the adjusting nut is possible in freely selectable spaced positions corresponding to whole number multiples of 1 mm. The slotted discs are effective to precisely keep this mm position. After the shafts 1 and 4 have been brought into the proper starting position by engagement of the bar 32, the bar is loosened and the adjusting step initiated. The interlocking members 35 remain in the slotted discs 34 during the positioning step and simultaneously function as an additional safety means against inadvertant rotation of the nuts consisting of two partial nuts 12 and 13.

This system of adjustment in whole number positions by means of the slotted discs 34 enables simultaneously an economical construction of a preselection system. This preselection system is likewise shown in FIG. 4. A rated value slide 36 for each tool is disposed on a carrier 37 provided with a scale. This rated value slide 36 is moved into a preselected position either manually or by known mechanical, pneumonic or electronic means. A series-connected signal processing logic 56 during production blocks the adjustment commands for the actual value slides so that all the preselection slides may be pre-positioned during production. At the slide 36 there are provided control sheets 38 and a selfcoiling band 39 extending in a direction away from the control slide. On a carrier 41 which extends in parallel with the carrier 37 there is arranged for displacement an actual value slide 40. The actual value slide has a leading portion 400 engaging in a groove 42a of a threaded nut 42 which is supported on a threaded spindle 43. This control transport threaded spindle 43 is connected with the transport shafts 1 and 4 via a connecting transmission 44 for exact angular rotation. The

than that of the tansport shafts 1 and 4 for reasons of construction, so that thereby the length of the preadjusting system is thereby correspondingly shortened. Air nozzles 45, 46 and 47 are disposed on the actual value slide 40 the last mentioned one of which is moved in the plane in which the band 39 extends during movement of the slide 40 along the carrier 41.

With the example shown in FIG. 4, the band 39 is disposed on the right-hand side of the rated value slide 36. The nozzle 47 is uncovered, and the logic connected with the nozzles supplies the logic decision that the actual value slide 40 is disposed to the left of the rated value slide 36. The control device then issues a corresponding control command with respect to the direction of rotation to the adjusting motor 21. If the nozzle 47 is to the left of the rated value slide 36, it is covered by the band 39 and the control motor receives a command which causes it to rotate in the opposite direc tion.

In FIG. 4, the rated value slide 36 is in its prepositioning position. When the positioning command is released, the parted guide arms loosen the frictional engagement of the parted nuts 12 and 13 with the shafts l and 4, respectively, in a direction as determined by the control nozzle 47, that means to the right in FIG. 4. At the same time, the threaded spindle 43 is rotated via the transport and tool shaft 1 and the transmission 44. As a result, the actual value slide 40 moves in a direction towards the rated value slide 36. When the first control nozzle 46 reaches the covering sheet 38, the transmission 20 is switched to slow speed by disengaging the coupling 19c and engaging the coupling 1%. The shifting operation is taken over by the seriesconnected signal processing logic 56 after the release of a dimension change command 64 past to said logic. If the sheetmetal then covers also the nozzle 45, the shifting transmission 19b, 20b will be shifted to 19a, 20a and thus the feeding speedis shifted to creeping speed. The threaded nut 42 which may be moved to and fro on the spindle 43 has connected thereto a slotted disc 48 provided with a number of slots corresponding to the ratio, same as the control slot 30, as well as the interlocking discs 33 and the slotted discs 34, and is interlocked via an interlocking arrangement 19 as long as an adjustment of the associated pair of toolcarriers is taking place. The interlocking arrangement 49 lead of the threaded spindle 43 may be kept smaller consists of a pivotally supported lever 49a and a pistonand-cylinder drive 49b. The coupling for the control transmission 19a, b, c and 20a, b, c, is opened and the brake 50 closed when the control slot disc 30 obtains a whole-number slot position before the indicator 31. With this, the rated value and actual value slides are in register, and the tool has reached the desired position. When the positioning step is completed, the interlocking arrangement 49 is released by the logic 56. As a result, the threaded nut 42 is freely movable on the spindle 43. No feed takes place any more. The threaded nut 42 is retained in its position by the actual value slide 40.

After the-tools have been positioned and the dimension changing step is completed, the signal processing logic 56 also loosens the interlocking means 32 and thus releases the tool shafts 1 and 4 for production.

Preferably, the tool shafts l and 4 carry only grooving or only cutter tools and there are provided several pairs of upper and lower tool shafts. Owing to this feature, a higher cutter speed is possible. The shafts of a pair may also have different lengths.

In the following, now, the adjustment of a pair of cutter tools is to be described in connection with FIG. la. After positioning, the shaft 4 is moved in a direction towards the shaft 1 through such a distance that the tools 5 overlap. The part 12 may advantageously be designed in such a manner that it acts as a supporting ring maintaining the web 26 in a horizontal position during the cutting operation. A smooth-edged cut is obtained as a result of this feature (please see 12a in FIG. la). As already stated in the introduction, shaft 1 is then moved in such a manner that the cutter 5a may contact the counter cutter 5b with the cutters moving toward each other under tension. This is shwon in FIG. la.

The device for displacing the transport shaft 1 is shown in FIG. 1. A displacing element 57 is fastened on the shaft journal 1a, said element comprising a marginal recess. A displacement lever 59'has one end engaging in said marginal recess, said lever being fastened at the machine stand by its other end. This lever 59 is connected with the piston of a piston-and-cylinder drive 60. The shaft 1 may be moved back and forth in its bearings by actuation of the piston-and-cylinder drive 60. In order to maintain permanently a positive rotary connection between the shaft 22a and the shaft 1, there is a key arrangement 61 provided between the two shafts which permits of axial displacement of the two shafts relative to each other. It is possible to use here any other arrangement allowing for axial displacement of the shafts relative to each other.

As the guide arms 15a and 15b which are pivotally connected with each other are moved back and forth on the transport shafts 1 and 4 the distance of the individual pairs of guide arms from the machine stands 2 and 3 differs.

The pair of guide arms 15a, 15b disposed nearest to the machine stand 3 in FIG. 6 which cooperate with the transport shaft 1 are connected via a hose line with a source of compressed air 66. A line 67 leads from the source of compressed air 66 to a control valve 68 which is adapted to be actuated electromagnetically, for example. The control valve 68 is connected with the piston-and-cylinder drives 17 and the vpiston andcylinder drive 51 via a flexible hose line 69, for example, said drives cooperating with the guide arms 15a and 15b. The hose line 69 is guided between the control valve 68 and a first deviation roller 70 rotatably supported in the machine stand 3 via a disc 71 also rotatably supported in the machine stand. The disc 71 is supported on a driven shaft 72 simply through loose frictional engagement. At the disc supported in the upper portion of the side stand 3 according to FIG. 6 the shaft 72 rotates in a counterclockwise direction. Looking from the deviation roller 70 the hose line 69 is coiled on the outer periphery in a thickness of one layer and a half, for instance, and is fastened at the disc 71 at 73 by a simple clamping arrangement which does not negatively influence the passage through the hose line 69. Looking from this clamping point the hose line 69 is once more passed around the shaft 72 and then is suspended in a very loose loop 69a between the shaft 72 and the valve 68. From the deviation roller 70 the end of the hose line leading to the guide arms is once more guided over a further deviation roller 74, so that the hose line extends from there in parallel with the axis of the transport shaft 1.

The control valve 68 is connected via a hose line 75 with the corresponding hose line 69 of a disc 71 arranged in the lower portion of the machine stand 3. In the case of the lower disc 71 the deviation rollers 70 and 74 are arranged above the disc 71 so that the loop is guided between the end of the line 75 and the clamping arrangement 73 on the lower disc 71 in a different way. As the pairs of guide arms a and 15b cooperating with the pairs of tool carriers on the shafts 1 and 4 are biased in the same sense, only one control valve 68 need be provided which enables fluid under pressure to be communicated to the two discs 71. The one half of the pairs of arms is controlled from the right, while the other half is controlled from the left.

As may be seen from FIG. 7, it is possible to arrange several discs 71 side by side on the shafts 72 in the form of a transport barrel for the transport of the flexible hose lines 69, said hose lines having associated thereto one control valve 68 each on an upper and a lower disc 71. If the guide arms disposed nearest to the machine side stand 3 are supplied with fluid under pressure through hose lines 69 to be coiled in the machine stand 2, then the hose lines will be in the condition as shown in the machine stand 3. The discs 71 in the side stand 2 are biased in a clockwise sense owing to the loose frictional engagement. The right-hand transport barrel (FIG. 7) supplies the guide arms of a grooving shaft and the lefthand one supplies the guide arms of a cutter shaft. There are more grooving tools available than cutter tools.

If, now, the guide arms adjacent the machine stand 3 move from right to left on the shafts l and 4, the hose lines 69 are withdrawn from the associated discs 71 in the right-hand machine stand against the effect of the frictional engagement, while the hose lines 69 are being coiled on the left-hand coils 71 as a result of the frictional engagement. The loops 69 at the right-hand discs are shortened while corresponding loops are forming at the left-hand discs. In this manner it is guaranteed that the lines always remain taut between the discs 71 and the guide arms, that means that no sagging loop can form, between the deviating rollers 74 and the associated guide arms.

Preferably, there are provided for one machine two devices in accordance with the invention (Building unit I and Building unit II) in which all the tool carriers or pairs oftool carriers each have associated thereto a rated value setting means and in which all the tool carriers moving in one direction are simultaneously adjusted and set one after the other. The operational step of adjusting the building units runs off in such a manner that there is one complete set of rated value setting means available for each building unit. If building unit I is in its position for operation the tool shafts of building unit II are moved away from each other and out of function.

The building unit shown in FIG. 5 comprises four transport shafts: the one pair P1 of transport shafts, for instance, is equipped with grooving tools 6 and the other one P2 is equipped with cutters 5. Owing to the arrangement of the different tools on different pairs of shafts it is possible to drive the cutter shafts in such a manner that the peripheral speed of the cutters is greater than the transport speed of the web, whereby an improved cut is obtained. The peripheral speed of the grooving tools is adapted to the speed of the web. With a machine having two building units there are thus provided altogether two building units each having two pairs of shafts, that is a total of eight shafts. Building units with only one pair of shafts are also possible if only a grooving or cutting is performed. The shafts of the building unit shown in FIG. 5 are not in function. The clamping plates 18a and 18b, in the case of the upper guide arms 15a and 15b, are disposed in rear of the arms, while in the case of the lower arms they are disposed in front of said arms. With this arrangement one can do with one die for the clamping plates.

At this building unit, now, the corresponding rated value setting means is positioned according to an adjusting ruler for each tool carrier. After completion of this positioning step, the positioning of the tool carriers is initiated by feeding the dimension changing command into the signal processing logic with the shafts still in their drivenapart position. In this operation, then, all the actual value slides with their three nozzles each are moving in the direction of their associated rated value setting means until the tool carriers have reached their proper position. The actual value setting means which first reaches its rated value setting means momentarily stops the adjusting step via slow or creeping speed to a standstill. Subsequently, the adjustment is automatically continued again via the overdrive speed through the logic until the next actual value setting means has reached its rated value setting means. The adjusting operation is started anew until the last actual value setting means has reached its rated value indicator. In this operation, all the tool carriers are simultaneously adjusted within a short period of time and are step-wisely brought into the exact position. Owing to this system it is possible to obtain a short adjusting time for the adjustment of all the tool carriers. It is to be borne in mind that all the rated value setting means are positioned prior to performing the actual adjusting step. The change in the sense of rotation of the shafts (moving 'to the right and moving to the left) results in short resetting paths and thus also short times of adjustment.

It is possible with the device in accordance to the invention which comprises only the smallest possible number of structural parts, to position the tool carriers, the cutting and grooving tools safely and quickly with a degree of positioning accuracy which will be completely sufficient for all the cutting and grooving operations in question.

What is claimed is:

1. Apparatus for longitudinally working a moving web having a path of movement comprising, in combination, a frame, the web moving through said frame, a tool shaft rotatably mounted upon said frame having an axis transversely disposed to the web path of movement, threads formed on said shaft, threaded tool supporting means mounted on said shaft cooperating with said shaft threads for axial adjustment upon said shaft, said tool supporting means including locking means selectively locking said tool supporting means upon said shaft, a tool mounted upon said tool supporting means adapted to engage the web, retaining means selectively retaining said tool supporting means from rotation with said shaft, adjustment drive means selectively drivingly connected to said shaft for rotating said shaft, and control means controlling operation of said drive means and said retaining means to produce relative rotation between said shaft and tool supporting means about said shaft axis to axially position said tool upon said shaft.

2. Apparatus for longitudinally working a moving web as in claim 1, a second tool shaft rotatably mounted upon said frame having an axis transversely disposed to the web path of movement, threads formed on said second shaft, second threaded tool supporting means mounted on said second shaft cooperating with said second shaft threads for axial adjustment upon said second shaft, secondlocking means selectively locking said tool supporting means upon said second shaft, a second tool mounted upon said second tool supporting means adapted to engage the web at a position in opposed relationship to the first tool, second retaining means selectively retaining said second tool supporting means from rotation with said second shaft, drive means drivingly connecting said second shaft to said adjustment drive means, said control means controlling operation of said second retaining means to permit relative rotation between said second shaft and said second tool supporting means about said second shaft axis to axially position said second tool upon said second shaft. I

3. Apparatus for longitudinally working a movable web as in claim 2 wherein said first and second tool supporting means and tools are simultaneously axially positioned upon their respective tool shafts.

4. Apparatus for longitudinally working a moving web as in claim 1 wherein said tool supporting means comprises a nut having first and second threaded portions threadily engaging the threads of said tool shaft, and biasing means interposed between said nut portions producing frictional engagement between said portions and said shaft.

i 5. Apparatus for longitudinally working a moving web as in claim 4 wherein said biasing means comprises a plurality of compression springs.

6. Apparatus for longitudinally working a moving web as in claim 4, annularly arranged notches defined upon one of said nut portions concentric with the axis of said shaft, said retaining means comprising a detent selectively engaging with a notch to prevent rotation of said nut with the associated tool shaft.

7. Apparatus for longitudinally working a moving web as in claim 6 wherein two detents are defined upon said retaining means associated with said nut, said retaining means including a pair or pivotally connecting arms, a detent being mounted upon each arm.

8. Apparatus for longitudinally working a moving web as in claim 1 wherein the thread defined upon said tool shaft includes a flank substantially radial with respect to said shaft axis, and a flank obliquely disposed to said shaft axis.

9. Apparatus for longitudinally working a moving web as in claim 1 wherein said control means includes an adjustable element, and a feedback element, said feedback element sensing the position of said adjustable element rendering said control means inoperable upon said feedback element indicating a tool position attained as determined by said adjustable element.

10. Apparatus for longitudinally working a moving web as in claim 9 wherein said feedback element includes a plurality of air nozzles, and said adjustable element includes means for restricting airflow through said nozzles.

11. Apparatus for longitudinally working a moving web as in claim 1 whereinsaid control means includes multiple speed transmissions interposed between said drive means and said tool shaft for rotating said tool shaft during adjustment at variable speeds in dependence with the position of said tool upon said tool shaft.

12. Apparatus for longitudinally working a moving web as in claim 11 wherein said control means includes reversible means for rotating said tool shaft in opposite directions during retention of said tool vsupporting means against rotation by said retaining means. 

1. Apparatus for longitudinally working a moving web having a path of movement comprising, in combination, a frame, the web moving through said frame, a tool shaft rotatably mounted upon said frame having an axis transversely disposed to the web path of movement, threads formed on said shaft, threaded tool supporting means mounted on said shaft cooperating with said shaft threads for axial adjustment upon said shaft, said tool supporting means including locking means selectively locking said tool supporting means upon said shaft, a tool mounted upon said tool supporting means adapted to engage the web, retaining means selectively retaining said tool supporting means from rotation with said shaft, adjustment drive means selectively drivingly connected to said shaft for rotating said shaft, and control means controlling operation of said drive means and said retaining means to produce relative rotation between said shaft and tool supporting means about said shaft axis to axially position said tool upon said shaft.
 2. Apparatus for longitudinally working a moving web as in claim 1, a second tool shaft rotatably mounted upon said frame having an axis transversely disposed to the web path of movement, threads formed on said second shaft, second threaded tool supporting means mounted on said second shaft cooperating with said second shaft threads for axial adjustment upon said second shaft, second locking means selectively locking said tool supporting means upon said second shaft, a second tool mounted upon said second tool supporting means adapted to engage the web at a position in opposed relationship to the first tool, second retaining means selectively retaining said second tool supporting means from rotation with said second shaft, drive means drivingly connecting said second shaft to said adjustment drive means, said control means controlling operation of said second retaining means to permit relative rotation between said second shaft and said second tool supporting means about said second shaft axis to axially position said second tool upon said second shaft.
 3. Apparatus for longitudinally working a movable web as in claim 2 wherein said first and second tool supporting means and tools are simultaneously axially positioned upon their respective tool shafts.
 4. Apparatus for longitudinally working a moving web as in claim 1 wherein said tool supporting means comprises a nut having first and second threaded portions threadily engaging the threads of said tool shaft, and biasing means interposed between said nut portions producing frictional engagement between said portions and said shaft.
 5. Apparatus for longitudinally working a moving web as in claim 4 wherein said biasing means comprises a plurality of compression springs.
 6. Apparatus for longitudinally working a moving web as in claim 4, annularly arranged notches defined upon one of said nut portions concentric with the axis of said shaft, said retaining means comprising a detent selectively engaging with a notch to prevent rotation of said nut with the associated tool shaft.
 7. Apparatus for longitudinally working a moving web as in claim 6 wherein two detents are defined upon said retaining means associated with said nut, said retaining means including a pair or pivotally connecting arms, a detent being mounted upon each arm.
 8. Apparatus for longitudinally working a moving web as in claim 1 wherein the thread defined upon said tool shaft includes a flank substantially radial with respect to said shaft axis, and a flank obliquely disposed to said shaft axis.
 9. Apparatus for longitudinally working a moving web as in claim 1 wherein said control means includes an adjustable element, and a feedback element, said feedback element sensing the position of said adjustable element rendering said conTrol means inoperable upon said feedback element indicating a tool position attained as determined by said adjustable element.
 10. Apparatus for longitudinally working a moving web as in claim 9 wherein said feedback element includes a plurality of air nozzles, and said adjustable element includes means for restricting airflow through said nozzles.
 11. Apparatus for longitudinally working a moving web as in claim 1 wherein said control means includes multiple speed transmissions interposed between said drive means and said tool shaft for rotating said tool shaft during adjustment at variable speeds in dependence with the position of said tool upon said tool shaft.
 12. Apparatus for longitudinally working a moving web as in claim 11 wherein said control means includes reversible means for rotating said tool shaft in opposite directions during retention of said tool supporting means against rotation by said retaining means. 